Fluid volume control



2 Sheetsa-)Sheet l J. W. TAYLOR ET AL FLUID VOLUME CONTROL Filed July 30, 1928 March 22, 1932.

March .22. 1932.

J. W.'TAYLOR ET AL FLUID VOLUME CONTROL Filed July 3o, 1928 2 Sheets-sheet 2 P l3e 4i215 :25 Z IZZ l i5 '2.4 175 4j f Patented Mar. 22, 1932 narran; STATES PATENT oFFicEl JAMES W. TAYLOR AND WILLIAJNI MEADE WHELESS, OF SAN ANTONIO, TEXAS FLUID VOLUME CONTROL Application filed July 30,

This invention relates to the control of the flow of fluid and has for its purpose the con- Jtrol of the volume of compress-ed fiuid iiowing through a conduit. It is intended primarily to be used in fiowing oil wells by pneumatic means, but may be used in various other ways wherever the same purposes are sought.

it has been designed with a view necessita ting apowerful spring under high tension to actuate the diaphragm ,as the pressure fluctuated on its inner area. lThis perniitted of little movement of the valve mechanism controlling the flow of fluid, the result being a l ocking or closing of the valve under slight variation of the fiuid pressure. f

For instance, devices of this character are n in demand for use in the fluid lines when the flow space he manner flowed by what is commonly known This consistsv in restricting as to allow the well to accumulate a headY of oil in the lower part of the hole. W'hen the oil has risen to a certain height in the bottoni of the well it will begin to meet with the increasing gas pressure, and this will continue until the pressure of the gas r has become greater than the liquid pressure in the well. when the oil .will be forced down and around the bottom of the inner string of pipeby the rising gas pressure.

When

ch a d from the well.

This method is employed where the `well steady flow.

rodum'ne` sufficient oi to maintain rihis Abein@- truc. .it will be readily seen that th ere is a heavy loss of after each hea d, which is due to the absence of oil in the `bottoni of the well to prevent its escape.

The result is that there is a sudden 1928. Serial No. 296,224.

drop of gas pressure in the well after each. head, this often. being as great as 7 5% of the pressure required to discharge the head of oil. It is at this point that the need to control the flow of gas arises, and it also becomes evident that any device used to control the flow must be adapted to wide variations in pressure.

It has been ascertained by experimentation what the flow of a compressed iiuid through any given sized orifice will be under a fixed and unvarying pressure. For instance, it is found by maintaining an absolute pressure yof 5 ibs., i. e., a pressure of 5 lbs. per sq. inch above atmospheric pres` sure., and allowing the gas to flow into the atmosphere, that 247 cu. ft. of free gas will flow` through a 1 orifice e'ach'ininute. By free gas is meant gas at atmospheric pressure. It has also been found that the rate of flow through an orifice increases or de. creases in almost direct proportionto the increase ordecrease in the size of the orifice.

It is an easy matter to gauge or control the flow of fluid through any given sized orifice, so long asv there is no fluctuation of pressure on either side of the orifice.l yIf the pressure on the upstream side of the orifice, i. e.,V the side from which the flow is coming, be 100 lbs. per sq. in. and the pressure on the opposite downstream side be 90 pounds, then there will be a pressure differential of ten pounds, and the flow will remain the saineas long as there is no change in pressures.

However, in a case as iust outlined, if the pressure on either side ofthe orifice fluctuates. the flow of Huid will change accordingly. If the pressure on the upstream side of the orifice drops to 90 pounds,'then the flow will ceasel entirely. Or if the pressure on the upstream side remains at 100 lbs., and the pressure on the downstream side drops to 80 lbs., then there will bev a difference of 20 lbs., iny pressure and the flow will. of course, be much greater than under the l() lb. differential.

In view of the foregoing, it is plain that the pressure on the upstream side of the orifice must be held fixed; and that provision must be made for a widely varying pressure on the opposite side, if the volume of gas flowing through the orifice is to be controlled Vunder actual working conditions.

Assuming that the available gas or air pressure is greater than that with which it is desired to flow the well, any pressure regulator, of rwhich there are numerous makes on the market, ma be used in the pipe line supplying gas to tile apparatus herein'jcontemplated to maintain a fixed pressure in the line between the pressure regulator and the control. The capacity of the pressure regulator will always be sufficient to assure an adequate supply of fluid to the control, although the latter may be operating to capacity. The pressure regulator may be omitted where the gas pressure is maintained steady by the compressor.

With a 'fixed and unvarying pressure assured on the upstream side of the orifice, the next step is to provide an orifice the size of which will, in effect, increase or decrease in accordance with the variation of pressure on its opposite or downstream side, or the'side adjacent to the well.; an dalso provide against closing or locking of the control mechanism,

regardless of the extent to which the pressure Y may'dro'p whenithe well heads. Itis an objectof the invention to embody these new and desirablerfeatures in. an apparatus.

A Since it is desirable that the volume .of gas flowing through the control be known at all l times, it is anobject to provide visible means also for indicating with a reasonable degree of accuracy the rate of flow, regardlessof theV pressure being carried in the gas ory air lines. This consists, broadly, of a mechanism that indicates at all times the size of an adjustable orifice, thelatterfbeing placed at an appropriate point in the device. c f

Withthese Vand other objects in view, as

Vwill appear as the'V description proceeds, the

, invention consists in thek novel features of construction andpcombination of elements.

v Fig.

' Fig. 4 isa sectionalview onthe plane 4--4 *Y 4ofF-igxQ.V n f' Y Fig. isan assembly view showing the de? vice connected within afiuid pressure'line sembly the. use of which is contemplated, a'

4rThe device is intended for inserting within aflowline for the pressure fluid and between the 'pump or ycompressor and the pipe leading into the wellor at any other place where fluid pressureis'desired. In Fig. lis shownjan as` pipe being understoodl as leading from the source of fluid under pressure.' The port B YV1,850,423 Y the port A by way of asafety valve indicatn ed at VF and a regulating valve C to the control D and from there to the outlet port B. Directly betweenV the two ports A and B a re lief valve E maybe employed.

' The safety valve adjacent the port A com prises a sleeve 14 extending longitudinally of a pipe 3 and havingat its lower end a fiange 1 fitting closely against the inner walls of the pipe 3 zand .having the passages 2 therethrough for the pressure fluid. There is a central passage 4 from the lower end of the tube 14leading to a valve seat 7 closed lby a ball valve 5. Said valve is held normally seated by means of a weight 8 resting thereon and it is to be understood that this weight may be regulated to hold the valve 5 closed with a predetermined pressure. The upper end of the tube 14is`connected by a nipple 9 to a plug 13. Said plug 13 has an L shaped passage 11 thereto into which the nipple 9 is screwed. A passage l0 through the nipple which an youtlet conduit 12 is connected. The

said conduit makes connection' with the cony' trol mechanism'L Das will be later described.

The plug' 13 has a plurality ofpassages 15y extending longitudinally thereof and connecting with a chamber 16 Vwithin the regula-` tor C. Said regulator includes a tubular member having at one side thereofa threaded opening in ywhich is screwed a stuffing box 17 within vwhich a stem'y 22 is rotatable. There is a packing 19 about said stem and a spring 18 within the box bearing, against a washer 20 and acting to com ress'the packing about the rotatable? stem. ygland 2l on they outer side of the stuliing boxy may be employed to adjust the pressure upon the packing. YThe spring18 normally holds thel packing under pressure, tending to ltake up ordinary wear.

The stem'22 is connected at. its inner end l witha valve member 23. Said valve member has asocket in which the ystem 22 is connected, said stem being held therein by a transverse pin 24. VAdjacent the stem 22 the valve member is provided with a chamber extending longitudinallyof the valve and having a lateral orifice 25 therein, from whichV ports27 lead to the interior of a chamber in the valve housing .30. Within said chamber is a transverse disc 29,'having openings 28 therein and a central threaded opening within lwhich the threaded end 7 6 of the valve is screwed. The said threaded end extends beyond the disc'a material distance and is held at'its endby a nut 3l which may be fixed upon f the valve stem and sleeves to limit the motion ofthe valve in' one direction.

TheV end of the valve housing y30 adjacent the valve stem 22 is extended inwardly about the valve forming an approximately fluid- 'lou tight enclosure a, through which no appreciable amount of liuid may pass. This flange serves to close the space between the chamber 16 and the chamber 29 within which the valve is movable and when the valve is screwed into the sleeve 30 as shown in Fig. 1 the orifice 25 will be closed. When, however, the valve is unscrewed by means of the stem 22, the orifice will be gradually advanced into the chamber 16, allowing the fluid to pass from said chamber into the chamber 29 in an obvious manner.

, The dial chamber 29 is connected by a cou-V pling with a pipe 26 which leads by way 03": the pressure control to the outlet passing to the well. The pressure control comprises a iitting connected with a pipe 26, having therein a chamber 87. The lateral opening in this chamber provides a connection with a special coupling 72, threaded at its inner end within a tube 51. The coupling 7 2 has a plurality of longitudinal channels 44 therein, away from the central axis of the coupling, these channels leading to a chamber 45. The coupling 7 2 has an axial passage therein with a central chamber 7 9a. The inlet end leading to this chamber is provided witha valve seat 42 which has a driving it at 98 Within the end of the coupling, this seat being adapted to receive a tapered head ,41 of a valve member. The upper end ot the chamber is closed by a flange 40 except for the plurality of openings 7'? leading from the chamber 45 to the interior of the pipe 51.

The valve 41 has a stem 33 thereon, extend` ing through the pipe '5l and through a. housing 52 for an expansible pressure member 32. Said housing 52 is connected at its inner side to a nipple which is screwed within an opening in the pipe 3, as will be seen from Fig. 1. A passage '.78 in said nipple is closed on the side adjacent the lhousing 52, except for a central opening in which a bushing 86 is screwed. This bushing has a. passage through which the valve stein 33 may pass, acting as a guide for said valve stem and also allowing a passage for the pressure fluid from the pipe 3 into the interior of the diaphragm 32.

Within the housing 52 the pressure member 32 previously referred to is located. lt is made up of a series of discs connected together in pairs at their outer margins and having a central opening through each set ot discs to which the discs are welded. Thus there is a passage centrally through the discs for the valve stem and the valve stemis slidablv free therein A bellows arrangement, which allows maximum movement ot the stem 33, is thus provided into which the pressure fluid may find access. The inner one of the bellows sections is connected at 36 witl the bushing 36. The opposite end of the bellows is connected to a stop member 35 screwed upon the valve stem atk 87 and serving not only to close the pressure memberj32 at that end, but also as a stop for a spring 39 surrounding the valve stem and pressing at its other end against a flange 40. This spring is under a predetermined pressure and tends to prevent the head 41 from closing the oriticeV 42.

The outlet end ot the chamber 79a is con nected with member 46 which serves as a lil@ ting connecting the interior thereof with a laterally extending ltube 47, the end ot which is welded at 49 with the forward end ot a connecting member 48. The fluid passing through the connecting member 47 will pass into the pipe 50 and from there to the port B.

The relief member E acts as a by-pass directly from the port A to the port B and serves the purpose of allowing a passagedirectly to the port B; when the pressure within the assembly exceeds a predetermined amount it acts to eliminate the possibility ot rupturing and bursting any part of the diaphragm 32 should a volume of gas under extraordinarily high pressure be suddenlyV applied to the control device and for other purposes as will be later seen. There is a bushing 57 screwed within one end of the housing 56 for this member, said bushing having a central passage leading rfrom the connecting pipe 99 to a valve chamber, said valve chamber is an extension 57 upon the bushing 57 and it is closed at its forward end by a plug 60. A valve seat 58 is iittedwithin the inlet end of the' valve chamber to accommodate a ball `valve 59, said valve is held within the seat by means of a spring 62, having'at each end thereofa bearing member or 64. Said spring may be adjusted as to tension by means of a threaded shaft 61, extending axial-` ly through a plug 60 and bearing upon the member 64. There are lateral openings 66 in the valve chamber leading to a passage 655 through which the fluid may pass tothe chamber 67 adjacent the outlet port B.

Referring to F ig. 1 and disregarding the spring 39, it will be noted that if the `internal area of the diaphragm 32 be four sq. in., and the pressure be lbs., the total pressure tending to .torce the valve-head 41 forward will be 400 lbs. This will ot course :torce the valve 41 into the orifice 42 and close the chamber 45 to the escape oi gas through said orifice 42. Assuming further that the area of the orifice 42 is 1 sq. in., it will be seen that it 100 lbs. pressure now be applied to the exterior of the diaphragm 32 through the chamber 45, that the total force tending to move the valve-head 41 out or" the orifice 42 will only be 300 lbs.; for the reason that the effective outer area of the diaphragm 32 is reduced to the extent ot the orifice 42. ln other words, with 100 lbs. ot gas pressure on either side of the diaphragm ein, the total force tending to close willbe greater by 100 lbs. than the total torce tending to open.

course, remain in closed position.

the orifice 42 being 2,5% of the area of the in-V terior of the diaphragm 32, the totalV` effective areaitending to open the valve 41 is less by 25% than the total elfectivearea tending to hold it in closed position; for the areatending to close will be 4 sq. in., whereas that tending ,to open will be 3 sq. in.

If now, 100 lbs. tension be placed on the spring 39,V the valve 41 would still remain closed for the reason that the spring pressure of 100 poundsplus a total of 300 pounds gas pressure on the external side of the diaphragm, would just equal the 40.0 pounds pressingV against vthe interior of the diaphragm, from the entry 7 8.

Butshould the tension on the spring now be increased to 115 pounds, Athetotal force tending `to open the valve will be 415 pounds. whereas the total force tending to hold it in closed position will still be 400 pounds. Un-

der these conditions the valve-head 41 will f move outv of the orifice/42 far enoughto permit'the escape of 5 lbs. per sq. in.,of gas pres# sure from the chamber 45 via the ,orifice 42; and ysince the exterior of the diaphragm 32 communicatesywith the chamber 45, through the or1fices 77, this pressure will also have been removed from its exterior, thus restorlng an equilibrium between the forces tend mgtonopenand those tending to close.y

open the valve 41; the effect of this was as though lbs. per sq. in. more ygas pressure had been added to theV exterior of the dia'- pliragm than wasbeing exerted on rits interiorgand the result of 4this was that the valve 41 released 5 lbs. per sq. in. gas pressure, or a total pressure of lbs. from they exterior kofthe diaphragm to restore a bal-V ance of ythe two forces controlling its move.- ment. Thls vmeans that the pressureV 1n the chamber 45 has now dropped to 95 lbs, per

*as `between the pipes 3 and the chamber 45` will be determined at all times by the excess tension on the spring 39. If the total tension on .the spring be 130 lbs., and the gas.

pressure remain at 100 lbs., vthen there will be anexcess pressure of lbs. tending toopen the valve. Thisin turn will mean that 10 lbs per sq. in. in gas pressure will be released lby the valve 41, or a total of 30 lbs., and that:

the pressure in thechamber will drop ,to 90 lbs. per sq. infinstead of'95 lbs. Y j Y c f f With 115 lbs. tensionV on the spring 39, when the valve-head 41 has been forced 'out of the `orifice 42, it will have moved onlyfar enough away from the Vorifice V42to `permit the escape of 5lbs. per sq. in. of gas pressure from the chamber 41 and will stop in this position until there is a change in gas pressure. If 5v lbs. of gas pressure per sq. in. escaped whenthe valve 41 opened, then there would remain 95 lbs. Vper sq.y in. gas pressure in the chamber 45; for 5lbs. pressure from 3fsq. instotals 15 lbs.; and 15 lbs.-from'415 lbs. equals :400 lbs.; so that when the valve reaches this position the `force `tending to close Will equal the force tending'to open andthe valve will, as said before, stop at this point as long as there be no fluctuations in gas pressure. f v

Should the gas pressure in the chamber 45 tend to drop below 95 lbs. the valve-head 41 kwillrmove back into the orifice 42 and check the flow of gas to a point where 95 lbs. pressure would 'be restored to the chamber 45 for if the pressure inthe chamber 45 drop to 90 lbs. per sq. in., then the total force tending to' hold the valve in open position would be less by 15'lbs. thanthe force tendingto close; for 90 lbs. gas pressure times 3sq. in. equals 27 0 lbs. gas pressure plus 115lbs. spring tension equals385 lbs.; but the effective closingpressurewwould still be 100 lbs, gas pressureytimes- 4sq. in., or a-'total force of 400 Ibstending to close. Thus it is 'seen that the valve 411 will move back and forth to reduce or yincrease V'the area opened to gas flow throughtheforifice 42 in directproportion to the rise and fall of pressure inthe chamber c 45; and even though the gas flowing through 'orifice 42'be r`into ythe atmosphere, under the conditions just outlined', the pressurewould always remain'at 95 lbs.'per sq. in inthe chamber 45 ,and further, that a differenceof 5'1bs. per sq. in. will remain constant as be-j tween the entry 78 and the Ychamber 45.

ence in pressure as between the entry 7 8 and the chamber 45 will be determined by the tension on the spring 39. 'This tension will be predetermined' by the relative areas ofthe diaphragm 32 and the orifice-41, and will be placed on the spring when the apparatus is assembled. Further, the spring Will belong enough and resilient enough so as to prevent any appreciable increase of its tension when the diaphragm 32 expands to movethe valveV stem 33 forward. Y p Y Referring to Fig. 1,*it will require 1() lbs. per sq. in., against the ball valve 5 to lift the weight 8` and pass the lgas pressure through` the'conduit 12 to the housing over the diaphragm32. IJIowever,y it has been seen that ythe Vdifferencev inpressure as between the chamber 45 and theentry 7 8 will at no time ing conditions. And,.since there is communiy,cation between the chamber 45 and the hous- From this it will bev seen that the differ-f ybe in excess of 5 lbs., per sqfin., under operatf safety. *valve to the housing over thek diaphragm 32 when the apparatus is properly functioning. It, however, the orice 25 be closedand, through leakage at the valve 4l or other causes, the gas pressure in thehousing over the diaphragm 32 should drop to a point where there was danger or bursting the-'diaphragm, the gas willv then begin entering through the conduit l2 via the safety valve 5 to maintainpressure on the opposite side of the diaphragm 32. This is the only'tunction of the safety valve.

From the foregoing it is noted that with 100 lbs. gas pressure on either side of the diaphragm 32 and 100 lbs. tension on the spring 39, and with atmospheric pressure in the out let 79a., that the valve 41 would tend to close as shown in the drawing.

But, it' operating the device with 110 lbs. pressure and l0() lbs. tension on the spring, it is assumed that the gas will be iiowing into a well casing or other receptacle and that pressure is being carried on the oppositeside of the valve 4l in the outlet 79a. This being true, the automatic y-pass valve 59-will be set to open at 95 lbs. per sq. in., thus passing gas pressure to the outlet 79a through the pipe connection 67. So it will be seen that before the valve 4l could close,vthe by-pass will open and admit gas pressure to the opposite side of valve 4l at 79a through theconduit 47; for it has already been seen that the ditferen'ce in pressures as between the chamber 45 and the outlet 79a, must be 100 lbs. or more per sq. in. before the valve 4l will close. This being true, withgas pressure at 110 lbs., the valve 4l would never close, although the pressure as between the outlet 79a and the Chamber 45 may vary as much as 95'lbs. per' sq. in. For, it the pressure in theoutlet 79a drops below l5 lbs. the' by-pass begins admitting gas to the opposite side of the valve at 79a.

The pressure is in turn exerted back against the outer areaV of the diaphragm 32 through/the orifices 77,A thus causing the diae phragm to collapse and the valve 41 to assume an open position.

t will further be seen that by varying the areas and dimensions of the parts comprising the apparatus, thateven greater difierentials may be obtained. lBut, with the device constructed as herein described, the gasl pressure may be raised to any point without readjusting any of the parts, and still preserve the 'differential of 95 lbs. pressure on the inner side of the diaphragm be 300 lbs. per sq. in., this pressure will also be transmitted to the outer side ofthe diaphragm 32 through the chamber 45 and the orifices 77j In operation Fi (l the @as enters throu hV the pipe 3, thence through the perforations 2%2 and the passages 15e-l5 to the orifice 25.L

The stem 22'l will then be rotated and the orice- '25' opened to4 any desired point, by

For if the manner already described. Thus the operator may increase or decrease the size of the orifice 25 at will, by merely rotating the stem 22.

It has already been seen that, with the de` vice constructed to the dimensions given herein, there will be'aconstant difference 0135 lbs. pressure per sq. in. as between the pipe 3 and the chamber 45 when in operation, and, since there will be no restriction between chamber 45 and orice 25, the gas pressure Wilibe 5 lbs. less in the pipe 26 than Lin thev pipe 3; for the orifice 25 will be the restricting agency as between pipe 3 and pipe 26.

Thus it is seen that with gaslp-ressure at 100 lbs. there will be a difference of V5 lbs. pressure per sq. in. as between the upstream and the downstream side of oriiice 25; and that even though the gas flow be into theatrnosphere at 79a, with the pressure at 100 lbs. in pipe 3, 95-lbs., per sq. in. pressure will be constantly maintained in the pipe 26. This means that while in operation there will at all times. be apressure greater by 5 lbs. per sq. in. in pipe3 than in pipe 26; for t-he pipe 26 and the chamber 45 have now become one,

and the same forces will control the rise and `tall of pressure in the pipe 26 as in the chamber 45. f i

Assuming that the pressure being carried inr the `apparatus is 100 lbs. and that the'gas isdischarging into the atmosphere at 79a, the pressure will then be 95 lbs. in the'pipe 26, for the orifice 25l will be restricting gas l Should the pressure tend to drop below 95:

lbs. in the pipe 26, the valve 4l'will move into the orifice 42 and arrest gas iow to a pointk where 95 lbs. per sq. in. would be maintained in the pipe 26.

Y being forcedout of therbearingSO in the i Itvthe size of orifice 25 be increased to ady mit more gas from pipe 3 to pipe 26, the pressure will tend to drop in pipe 3, but the pressure regulator will open to supply the increased flow. `With the increased flow the pressure will tend to `rise in the pipe 26, but then again the valve 4l will move out of the orifice 42 andpermit the gas toescape to a held in the chamber 45.

lt vhas been found'that under a 5V lb. difpoin-t where only lbs. per sq. in. will be 'ferenti'ah that is, a pressure greatervby 5 lbs.

per sq. in.non theupstream side than lon the i downstream side, that approximatelyOcu.

tt. of gas willtlow through al1/2 orifice each.A minute. 'If then the orice 25 be -1/2 in. in di-` ameter, it Awill lbe seen that with Athe rpressure.

in pipe 3 at 100 lbs. and the pressure in pipe f: tending toV close it. 'This would mean, of'

,y 26 at 951bs.,that approximately 60 cu. ft. will be lv.flowing through orifice each minute.

- B utbearing in mind that there is 95 lbs.V pressure in pipe-26, vand that thev gas is iowing kseenthat the valve.l y41 will vautomatically ymove in and out of the orifice 42'to increase or decreasetheareapopen to gas iiow from f chamber 45 to correspond to the'open area of orifice 25. lWith the pressure asjust outlined, thelarea open yto gas flow at 42 would be approximately 1/8 the'area ofthe orifice 25,

' lbs. pressure was maintained against the` since as much gas will flow through the smaller size into .the atmosphere under a 95 under a.5 lb. differential. Y If now'pressure in 79a, Fig. 1, begins to Vlb. differential las will throughthelargery build up,it would not diminish the flow of gas through the orifice 25; for the valve 41 wouldv recede into thechamber and increase the' open area of orifice 42 in exact ratio to the Increase ofpressure` inthe outlet79a, thus assuringthat the same volume Would .loeY

moving through the orifice 25 as when flowing .intoy thek atmosphere at V7 9a.A If, for instance,

the' pressure in 79a increases to 45 lbs.,-th is pressure would be exerted back. against valve head 41, thus reducing to that extent the force course, that the valve 41 would recede into the 'chamber 45; thus, as said before, increasing.

Vthearea open 'to ow at 42 in exact ratio to I the increased resistance'ofiered at 79a. Until 'there was pressure in 79a, valve 41 had reducedfthe outlety atk 42 to a point where 95 downstream side of orifice 25; but with 45 26 will remain the same as long as the presysure kin 79a remains below 95 lbs. Should.

oriice'25l is the restricting agency as between at 79a,u ity will onlybe restricted to the extent of50 lbsas between the chamber 45 andtheoutlet 7 9a, and the area open to gas lflow at 42y will loey approximately twice ,that

as withoutpre'ssure inY 79a. From this lit will beseen that, while the pressure may vary Y as between'theoutlet 7 9a and the orifice25, the volume of gas moving'gthrough the pipe the pressure in 79a rise above 95 lbs., the flow `wi-1l,'ofz course, then be retarded inthe pipe 26,r andthe volume of gas moving through 26wi11 diminish, for valve'4'1 will have ceased Y to function, ,due to an leq'ualizing of'theforces 1 f eo i by whichy itis"V actuated. Y

From the'fo' legoing `it will be yseen thatthe pip 3 and PPeIQG; ndthe valvell, by gaug- 1ngthe'volum'e,and maintaining a constant 5 density ofjfluid. on the downstream ,side of the orifice is `the factor that makes` itr prac` tical to indicate the :volume rof fluid flowing thru thedevice f g f y a It will be seen that, by changing the connections on the apparatus, vthe housing enclosing kthe diaphragm 32 maybe used in a vertical position and that aweightmay be substituted for the spring 39 and still obtain the same results as claimed herein. Y

Manually operated means are also provided to indicate the volume of gas flowing through the apparatus so Ythat one may know at any time the pressure'and the volumefof the gas flowing through the control mechanism. In Figs. 2, 3 and r4 the details of this indicator are shown. The indicator is connected'V dire'ctly to the chamber 30, Fig. 2, for the valve 23 vpreviously described. lfVithin; one side ofthe chamber 3,0 and adjacent the tapered part 102 ofthe said valve there is provided i a bushing112 which is screwed withinthe wall of thechamber 30 and extends laterally away from the chamber, providinga hous-` ingi'oi.1 a stem 111. vSaid stem is guided in its movement within the bushing 112, the in` rner end ofthe stem passing through a plug 116 which acts as a glandupon the packing 114 which is held kin position by means of a spring 113. 'This packing preventsyfthe escapeof pressure fluid past the stem 111 into the indicating mechanism. The bushing 112 is mounted within the lower wall 118 of the indicator housing 123. The upper end ofthe stem y111; passes through a plug 116 and fits within the cupped lower end of a member 120 the uppertapered end of whichV fits within a recess 121 of the lever 122. Said lever 122 ispivoted upon arthreaded ypin 17 5 sorvr whichV is, adjustablevwithin aV plurality ofv openings within the housing to vary the effect of therlengthof the lever 122 and the free end ofsaidlever is connected by'a link 124 Vwith the arm 125 of a bell-crank lever, the other arm of which isformed into aV rack or gear 125r which'meshes with a segmental gear 128 pivoted upon a pin-130. The free end of the lever 122 `is held resiliently downwardby los means of a spring139 pressing at its upper end against a stationary bracket in a :housmg and at its lower end upon anut and washer 140 at the lower. end-cfa rod extended through the endof ,the lever 122.

The gear v128 hassecured frictionally theretoan arm 131 held .uponthe' gear 128 by means of a' screw 132. The arm 131 has a socket 135 therein to receive the pointer 134 secured ad- .justably iny saidysocket `by means of a setV Y screw 136.v

The pointer 134will beicarried in the slot Y 135 and held in positiony bythe thumb-screw V136.; The coilspring 137 wil'l'at allgtimes preventlost motion in the pointer l134 in aman-y ner easilyy understood. It, will be seen that the y interior of the head`l20gisan invertedV cone,

rounded'at its smallerrfend;v this permits. a

rocking motion of the head 120 which in turn permits the stem 111 to travel in a direct line, although the notch 121 may tend to describe a circle in its upward and downward movement. In operation, there will be gas pressure in the member 30, which will tend to torce the stem 111 upward,- the spring 139 will counteract this force, and may be set to correspond to any pressure in 30 by the nut 1410.

Numeral 1111, F 3, is a shutter that encloses the mechanism and is clamped to the housing by thumb screws as shown at 143 in Fig. 2. Y

Numeral 144, Fig. 3, represents a glass portion of the housing. rlhe upaer edge or' the glass 111e will be circular and will lit into the circular portion of the housing' as shown at 146, Fig. 2; the upper and circular edge of the glass will lit loosely in the housing' 1116 as shown at 147, Fig. 3, and will be supported by its ends resting in the housing. The member 1&9, Fig. 3, is the bracketed dial shown at 150 in F ig. The dial carries the printed numerals and is made of any suitable material. A recess inthe housing receives and holds the dial in position as shown at 149, Fig. 3.

'lie travel of the pointer 13e may be increased or decreased by changing the position of the screw 175, Fig. 2, relative to the openings in the arm 122. rlhe packing lleimay he renewed by removing the screw 17 5, which in turn permits removal ot the head 120, when the gland 116 is screwed out of the member 11T. Gas will not escape while the packing is being replaced; for the beveled portion 176 on the member 111 will move into and seal the space 177 to the escape oi gas in a manner easily understood.

Assuming now, that the pressure being carried is 150 lbs., and that the stem 22, Fig. 2, has been rotated to the right to a. point where orifice 25 has been drawn into the housing 30. Orifice 25 will then be close-d to the flow oi through the member 30 g and the stem 111 will have traveled up the beveled face of 102 until it is in position on-the cylindrical portion of 23. r1`his upward travel of the stem 111 will have imparte-d a left hand movement to the pointer 134, causing the latter to swing around to the pressure column P on the dial 150, thus indicating that orilice 25 is closed to gas entry to the chamber 30.

ln computing the rates of flow herein, an orice l/S in diameter is taken as a unit of measurement, and 1000 cu. ft. of tree gas flowing through the orifice as the unit ot volume.

1f, for instance, the threads at 10'? be 16 per linear in., it will mean that for each complete turn of the stem 22 the member 23 would move in or out of orifice 30a l@ lin ear in. and

The mechanism actuating the pointer 134 will be coordinated with the horizontal movement ot member 23 in such a manner as to cause the pointer to move from the center of one column to the center of another, on the dial 150, with each complete turn of the member 22. 1r" the member 22 be rotated one complete turn to the right, it would cause the stem 111 to travel upward along the bevel face 102 this would mean, of course, that stem 111 had traveled a given distance in an upward direction. This upward movement of stem 111 will, as said before, be transmitted to the pointer 134 in such a manner as to cause the latter to move from the center' of one column to the center of another on the dial 150. From this it will be seen that the pointer will at all times indicate the open area of oritice 25.

1n the following, the number 15 is arbi trarily selected to represent one atmosphere as the unit of compression, and the exact igure (14.7, o E), disregarded.

, 1n operation, it is assumed, as point-ed out and described in preceding pages, that the apparatus is operating under a 5 lb. differential; that is, there is a dih'erence in pressure of 5 lbs. per sq. in. as between the upstream and the downstream side of the oritice 25.

It is found that under a 5 lb. dilierential, 3.86 cu. ft. of 'tree gas will liow into the atmosphere through a l/S orifice each minute, or a. total ot approximately 5,500 cu. ft. per 24 hours.

However, if free gas be compressed to 10 atmospheres, or 150 lbs. per sq. in. it will have been reduced to -115 of its volume at atmospheric pressure. 1f, then under a 5 lb. ditierential, and flowing into atmosphere, 5,500 cu. ft. of free gas moves through a 1/3 orifice in each 24 hours, when compressed to 150 lbs. and flowing against a pressure 5 lbs. less, or 115 lbs., it will be seen that 10 ltimes the volume of tree gas will be moving.

If compressed to 20 atmospheres, or 300 lbs. per sq. in., the volume moving would be approximately twice that moving under 150 lbs. pressure, assuming always that the ditferential of 5 lbs. as between the upstream and downstream sides of the oriliceis maintained. For it is found that for each unit of compression added, the volume of air confined is increased by the capacity of the receiver at atmospheric pressure; if the receiver holds'100 cu. tt. of tree gas or air then another 100 cu. ft. added would raise the compression one atmosphere or 15 lbs. per sq. in. Thus a pressure gauge reading of 150 lbs. will indicate that there is 10 times the cacompression started.

Thus it will be seen that the higher the degree of compression, the greater will be the volume of free gas moving through the orifice.

If operating the device under 150 lbs. pressure, then the member 22 will be rotated in a manner already described until the pointer 134 moves to the pressure column P. This will indicate that the orifice l is closed.Y Thefpointer 134 will then be moved out of the slot 135 until itis in the position with the lpointer resting in the pressure column .P and pointingto the first or lowest pressure brachet, that is 150., the pressure with which the apparatus is to be operated. If now the member 22 be rotated one turn to the left, the pointer 134 will move to ther position in the next adjacent column, V'and will rest in column I with its point at this will indicate that the orifice 25 has beenr opened to the equivalent of an orifice 1/8 in diameter, and that gas is flowing through at the'rate of 55,000 cu. ft. of free gas each 24` hours. If it be desired to double' the flow of gas, another left hand turn of member 22 sends the'pointer to column II, which indicates that there is the equivalent of two 1,/8 orifices Vopen to gasy flow, and that the volume moving through orifice 25 is now 111,000 cu. ft. per 24 hours. If the member 22 be rotated untilthe pointer rests in column IX, then it will indicate that there is the equivalent of nine 1/8 orifices open to gas flow'at 25, and that the volume passing through is Y 500.000 cu. ft. per 24 hours.

If the pressure now be raised to 325' lbs. the pointer 134 will be set to rest on the 325 lbs. bracket in column Rand the stem rotated until the pointer' indicates the desired flow. If the pointer rests as shown in the drawing, Fig. 2, then it will indicate that 509,000 cu. ft. of free gasis flowing through the orifice 25 each 24 hours and that the pressure being carried'is 27 5 lbs.

The diaphragm 32, Fig. 2, is only one form ofpressure operated means separating the pressure fluid chamber'78 from the chamber 45 and it is to be understood that other equivalent devices are contemplated at this point.

i By the useof this control the volumeofy air or gaseous fluid delivered to the well or other receptacle may be automatically controlled so that 'the operator is assuredof a uniform rate of discharge Vof fluid to the Well no matter what the back pressure in ,j the well maybe.

What we claim as new is:

" 1. In a device of the character described, a

flow4 line,`a valve chamber therein, a valve adapted `to fit an orifice therein, means t0 V deliver a predetermined flow of air to the upstream side of said orifice, and means to'control said valve to pass a predetermined vol-` urne of fluid'through said orifice regardless n of the amount of fluid pressure on the'downi stream side of said'orifice, means yto autosp`matically pass pressure' Huidl tothe down'-l stream side of saidl valve when there is a predeterminedV dierence of pressure on the opposite sides of said'orifice. f Y Y 2. A pressure fluid regulator device arranged to'maintain a constant flow of Huid i at varying pressures comprising a valve, a

discharge orifice,fmeans between said valve and said orifice to vary the size of orifice in proportion to the back pressure at said orifice.

3. A pressure fluid regulator including a regulator valve, a discharge orifice, a control valve for said orifice, andmeans yto balance said control valve whereby an equal quantity of fluid by'weight will pass both said regulator valve and said control valve at varying '80' said regulator valve to a constant differential pressure whereby a known quantity of fluid will passtherethru, means to subject said con? ytrol valve tothe downstreamv pressure of said Y regulator valve and to a variable back presf sure, and additional balanced means to operate said control valve to release a quantity of fluid equalVY to that passing said regulator valve regardless of the back pressure on 'said control valve. s 4

6; In combination with apressure fluid flow regulator-apparatus, means to measure the 'flow of fluid therethru at a constant predeterminedV pressure, and means subject to a variable back pressure to control the discharge of' fluid fromsaid apparatus ata rate equal to that of the measured flow.

7 In combination ywith a fluid pressure flow line, a regulator valve subjected to a constant differential pressure, a control valve subjected to a variable differential pressure, and means to actuate said control valve in response to changes in its differential pressure whereby the rate of flow of fluid thru both r,of said valves will be equal.

' In testimony whereof'we hereunto affix'our signatures this 20th day of July, A. D. 1928. JAMES W. TAYLOR.

w. M. wHnLnss.

ioo 

